dallas



Dec. 22, 1931. c. D. DALLAS COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheen l M v MW R Z 6 M/ W 202772655 many/Mg Dec. 22, 1931. c. D. DALLAS comma MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet 2 ZnvarzZaz" CFzazfaa I a l ds g 7/ Dec. 22, 1931. I c. D. DALLAS 1,837,209

COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet I5 ZZ/ZZ7ZE55 v I Dec. 22, 1931. c. D. DALLAS 1,337,209

COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet 4 wanes? I v C ZZF ZES DZYcZi ZdS Dec. 22, 1931. c. o. DALLAS 1,837,209

' 001mm mcamn Filed Dec. 2. 192s 1o Shets-Shaet e "ma/572 Cz'azifa Z7. ZlzZZai f Dec. 22, 1931. c. D. DALLAS 1,837,209

COILING MACHINE Filed Dec. 2. 1929 l0 Sheets-Sheet 7 [7242765 Zhs witness 22, 1931. c. 13. DALLAS 1,837,209

COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet 8 I ll/l CwrZa U DaZZas Q Dec. 22, 1931. c. D. DALLAS 1,837,209

COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet 9 Dec. 22, 1931. c, D. DALLAS 1,837,209

COILING MACHINE Filed Dec. 2, 1929 10 Sheets-Sheet l0 Patented Dec. 22, 1931 UNITED STATES PATENT 0FFICE CHARLE D. DALLAS, OF CHICAGO, ILLINOIS, ASSIGNOR TO REVERE COPPER AND BRASS,

INCORPQRATED, OF HOME, NEW YORK,

A CORPORATION OF DELAWARE COILING MACHINE Application filed December 2, 1929. Serial No. 411,106.

' through-is subjected to two opposite bending or curving operations, it being first curved downwardly over the first roller and then oppositely curved between the second and the third roller. These separate bending-operations are generally produced by placingtwo of the rollers in parallel spaced apart relation, preferably in a plane parallel to the direction of travel of the strip of material with the third roller positioned above the other two and nestingthe'rebetween in symmetrical closely spaced apart relation. By retaining substantially the same relative positions of the three rollers but mounting them so that the plane of the lower two rollers is inclined a substantial amount to the direction of travel of the strip, one of the bending operations is eliminated, and the desired curvature ,is imparted to the strip by a single bending operation. resulting in less friction and less likelihood of buckling of the strip of material as it is fed from the rolling mill into the coiling machine. I

One of the objects of the invention is the provision of a coiling machine of the kind de-' scribed which is operable to impart any desired curvature to a strip of material by a single bending operation, the spacing of the rollers and the angle of inclination of thegroup being so arranged as to produce the "desired curvature.

' quently rolled to great lengths,

In the rolling of sheets of strips of material, such as copper or brass, which are freit is especial ly desirable for convenience of handling, that such strips leave the rolling mill in the form of coils. In many cases the thicknessand rigidity of the metal thus coiled makes itdiiiicult to again insert the curved free end of the coil in the rolling mill. This difiiculty is overcome by leaving the outer free end of such strips uncoiled for a short distance, therebyiforming a so-called tail. Since the tail is straight the coil is thereby easily reinserted in a rolling mill for an additional operation, as more particularly described in my copending application, Serial No. 332,797,

' filed January 16, 1929 now Patent No.

1,779,115 granted Oct. 21, 1930, and another object of the invention is to provide improved mechanism operable for forming a straight tail on the free end of such'coils.

The strips of material so operated upon coil about themselves on a support provided for that purpose on one side or the other of the line of travel of the strips. The invention contemplates that theadvance of the strip and "the curving operation be terminated by lowering one of the rollers out of the path of the strip when the strip has passed substantially through the coiling machine thereby stopping the strip and'leaving the straight uncurved end between the rollers. In order that another strip of material may be fed into the rollers immediately following the release of the preceding strip from the curving operations, mechanism is provided which throws the coiled strip forwardly a suflicient distance to remove'the straight portion or tail from the machine. This mechanism includes a curved plate having a pivotal mounting forming a guide assisting the curved portion of the strip to coil about itself. By tilting the plate forwardly at a rapid rate the curved strip is thrown ahead sufiiciently that the tail portion is drawn clearof the rollers. The mechanism provides.

ly and to return the plate to its original position as a guide and connects other mechanism with the drive shaft to return the'roller to its original operative position relative to the other rollers. As a result of this sequence of operations the machine is then ready to receive another strip of material for coiling, and a further object of the invention is to provide improved mechanism operable to perform the above described sequential operations.

Another object of the invention is the production of a coiling machine of the kind described which is simple, convenient, compact, durable, reliable, efficient, and satisfactory for use wherever found applicable.

Many other objects and advantages of the construction herein described and shown will be obvious to those skilled in the art from the disclosure herein given.

To this end my invention consists in the novel construction, arrangement and combination of parts herein described and shown and more particularly pointed out in the claims.

In the drawings, wherein like reference characters indicate like or corresponding parts,

0 Fig. 1 is a front elevational view of the device;

Fig. 2 is an end elevational view of the device shown in Fig. 1;

Fig. 3 is a sectional view on the line 3-3 of Fig. 1;

Fig. 4 is a bottom plan view of the portable portion of the device;

Figs. 5 and 6 are sectional views on the lines 5-5, and 66, respectively of Fig. 4;

Fig. 7 is a section along the line 77 of Fig. 2;

Fig. 8 is a section along the line 88 of Fig. 7;

Fig. 9 is a section along the line 99 of Fig.

Fig. 10 is a view similar to Fig. 9 showing the roller in inoperative position;

F ig. 11 is a section along the line 1111 of Fig.

Fig. 12 is a section along the line 1212 of Fig. 11;

Fig. 13 is asection along the line 13-13 ofF1g.3;

. Fig. 14 is a perspective view of a disk serving as a cam;

Figs. 15, 16 and 17 are sectional views respectively along the lines 1515, 1616 and 1717 of Fig. 13;

Fig. 18 is a perspective view of adjacent fragmentary portions of the drive shaft and trip shaft;

Fig. 19 is a section along the line 1919 of Fig. 16; and

Fig. 20 is a perspective view of a strip of material formed in a coil with a tail on the outer end.

Referring now more particularly to the drawings, a front elevation of a coiling machine 20 embodying the devices of my invention is shown in Fig. 1 as portably mounted upon a rail 25 and a concrete base or support 24. A frame 21 provides a support for the operating mechanism including a motor 22, the frame being braced by a plurality of transversely extending webs 37 and longitudinally extending webs 38. A plurality of axles 28 are mounted underneath the frame 21, each carrying on one end a flanged wheel 26 operable to engage the rail 25 and on the other end a roller 27 positioned to roll along the concrete base or support 24.

The coilingv machine is manually movable to and away from its operative position in front of the rolling mill by rotating a wheel 39. The wheel 39 is operatively connected with two of the axles 28 by means of a system of gears and sprocket wheels. The wheel 39 is fixedly mounted upon one end of a shaft 40 so that' rotation of the wheel likewise rotates a pinion 41 fixedlymounted upon the shaft. The pinion 41 operatively engages a gear 42 mounted upon a shaft 43. A sprocket wheel 44 is mounted on one end of the shaft 43 so that rotation of the wheel 26 and of the roller 37 rotates the axle 28 and with it the supporting wheels 26 and 27, thereby causing the coiling machine 20 to move on the track comprising the rail 25 and the conv crete base 24. Increased tractive effect is secured by similarly rotating the end axle 28 by means of a sprocket chain 48 connecting a sprocket wheel 47 mounted on the intermediate axle 28 with a sprocket wheel 49 mounted on the end axle 28. By thus mounting the coiling machine 20 on a track, it is easily shifted into and out of operative position in front of a rolling mill and from one mill to another.

The coiling machine 20, when in its operative position is stationed immediately in front of a rolling mill, generally designated by the numeral 23. In the position shown in Figs. 1 and 2, the coiling machine is so situated that a sheet of material 33 passing between a pair of rollers 30 forming a part of the rolling mill, is directed into the coiling machine. The rolling mill 23 comprises a frame 29, providing a mounting for the rollers 30, and a pair of pivoted plates 31 forming a funnel shaped guide operable to direct the sheet of material 33 into the coiling machine 20. The free end of the lower plate 31 rests upon a portion of the'rolling mill frame 29 while the other of the plates 31 is suspended above the lowermost plate by means of an I rod or bar 32. The rolling mill 23 may be any type operable for performing the usual rolling operations upon strips of metal or the like.

The motor 22 is supported upon one end of the frame 21 and the driven mechanism, comprising the coiling machine 20, is mounted upon a pair of standards 34 and a standard 35. The standards 34 and 35 are fastened to the frame 21 by a plurality of bolts 36.

A dr ve'shaft 54 is operatively connected with the motor 22 by a series of step down gears. The shaft 54 is carried by the standards 34 and is journalled in a bearing .50 mounted on the upper end of the standard 35. The mechanism operatively connecting the shaft 54 with the motor 22 comprises a motor, shaft 55 having a pinion 56 mounted on the outer end in operative engagement with a gear 57. The gear 57 is mounted on a shaft 58 carrying a pinion 59. The pinion 59 operatively engages a gear 60 mounted on the end of the shaft 54. The shaft '58 is journalled at one end in a bearing 51 and at the other end in a bearing 61.

The shaft 54 actuates three rollers, respec tively numbered 62, 63, and 64 normally arranged as shown in Fig. 9. For this purpose gears 65 are fixedly mounted on the shaft 54 in mesh with a pair of gears 66 and 67, suitably mounted on the ends of the rollers 63 and 64 so as to actuate the rollers in clockwise direction, as observed in Figs. 2, 8, 9, and 10.. The roller 62 is rotated oppositely to the rollers 63 and 64 by idler gears 68 and 69 which operatively connect the gears 66 with gears 70 mounted on each end of the roller 62. The sheet of material 33 in advancing through the machine 20 passes under the roller 62 and over the rollers 63 and 64, and emerges with a permanent curvature causing the strip to coil about itself above I the aforementioned rollers.

The coil 53 as it forms is supported by a curved throw plate 76, an idler roller 67a. and a driven roller 67.

The spacing between the upper roller.62 and the lower rollers 63 and 64 is varied in a well known manner by providing a plurality of inclined. rods 72 and 73 operatively connected by beveled gears 74 with a manually operated wheel 71. The inclined rods 73 have threaded connections with frames 78 in which the ends of the roller 62 are journalled, thereby providing for varying the spacing between the roller 62 and the underlying rollers 63 and 64.

The rollers 63 and 64 are preferably of the same diameter and so positioned that their upper tangential plane is substantially inclined to the horizontal and upwardly in the general direction of travel of .the advancing strip of material 33. Such inclination may be made any desired amount, but I find in practice that aninclination of substantially 15 degrees produces the desired result for'the usual spacing of the rollers 63 and 64, inasmuch as the strip of material 33 is thereby enabled to pass both of the rollers 62 and 63.

without distortion. Bending of the strip is caused by contact of the under surface of the strip 33 with the periphery of the roller 64,-

the roller 62 cooperating to impart the desired curvature. -The strip of material 33 is directed over the roller 64 by a pair of members 98 mounted at opposite ends of the a so-called tail on the coil 53, mechanism is provided which causes the roller 64 to drop out of the path of the strip and to return to its operative position after, the strip has been removed from the machine. For this purpose, the roller 64 is mounted upon bearings 79 which are pivoted to rotate about the axial line of the drive shaft 54 as a center. The bearings 79 are operatively connected with a trip shaft 81. Each of the bearings -7 9 is provided with a lug 80 forming a pivotal connection for one end .of a link 83. The other end of the links 83 are pivotally connected with cranks 82 fixedly mounted on the trip shaft 81. The links 83, the lugs 80. and

the cranks 82 provide knuckle joints, which, upon slight rotation of the trip shaft 81 in counter-clockwise direction, as observed in Figs. 9 and 10, are broken down and permit the rollef 64 and the bearings 79 to move downwardly by reason of their weight. It is to be noted that rotation of the roller 64 and bearings 79 about the drive shaft 54 as an axis permits the gears 67 to remain in meshing relation with the gears 65 so that the roller 64 is rotated by the shaft 54 for all positions. The weight of the roller 64 and the bearings 79 carry the roller and bearings from the position shown in Fig. 9 to that of Fig. 10 wherein the link 83 and the crank 82 are shown in dotted lines.

The pivots connecting the link 83 and the lug 80 and the crank 82 lie above and to one side of. the line connecting the center of the trip shaft 81 with the center line of the roller 64 when the roller is in its normal operative position. The weight of the roller 64 there- 7 Atension spring 94, best shown in Fig. 8, A,

is so mounted'and connected with the trip shaft 81 as to assist in holding the bearings .7 9, cranks 82 and links 83 in their full line position and to yield to permit these members to take the dotted lineposition of Figs.

8 and 9 upon a slight rotation of the trip shaft 81.

The trip shaft 81 may be rotated in counterclockwise direction, as observed in Figs. 8, 9 and 10 by any suitable means. In Figs. 1 and 2, I have shown a rope or cord 91, fastened at one end to an. arm 90 which is mounted upon a wheel 88. The wheel 88 is fixedly mounted on a stub shaft 89 and rotation of the wheel actuates the trip shaft 81 by means of a sprocket chain 93. The chain 93 connects sprocket wheels 92 and 87, mounted upon the shafts 89 and 81, respectively.

The operator, by pulling on the rope 91 rotates the trip shaft 81 sufiiciently to break the knuckle joints connectin the bearings 7 9 with the shaft 81. The breaking down of the knuckle joints between the bearings 79 and the shaft 81 permits the roller 64 and bearings to be carried down by their own weight,

thereby rotating the shaft 81 in counterfly wheel 84 mounted side by side on the shaft 81 with the disk 85 on the near side of the fly wheel, as observed in Figs. 1, 9 and 10. The disk 85 is fixedly mounted on the shaft 81 and the fly wheel 84 is mounted to spin on the shaft. A plurality of roller bearings 115 enables the fly wheel 84 to be spun about the shaft 81 with a minimum of frictional resistance. A pin 96 is mounted on the near side of the flywheel 84 with the free end of the pin projecting through a segmental slot 97 formed in the disk 85.

By reason of the mass of the fly wheel 84, it is possessed of considerable inertia, which is further increased by a counter-weight 86 mounted on the fly wheel, diametrically opposite to the pin 96. The fly wheel 84 takes the position shown in Fig. 9 with the counterweight 86 at the bottom of the fly wheel when the roller 64 is in its operative position. The initial rotation of'the shaft 81 occasioned by a pull on the rope 91, carries with it the disk 85. Since the pin 96 normallybears against the end wall of the slot 97, rotation of the disk 85 carries the fly wheel 84 along with it to the position shown in Fig. 10. The fly wheel 84, being free to spin on the shaft 81, will rotate by its own momentum beyond the position shown in Fig. 10, following the initial movement imparted by rotation of the disk 85. ,7 The slot 97 limits the possible amount of rotation of the flywheel 84 relative to the disk 85.

Rotation of the fly wheel 84, as described, is utilized to actuate a clutch mechanism '106 connecting the trip shaft 81 with the main driving shaft 54 in such a manner that the trip shaft will be-rota-ted in a direction opposite to that occasioned by the pull on the rope 91 and will thereby return the roller 64' to its normally operative position. ,For.

this purpose a gear 101 is mounted to spin on a shaft 100, the gear being in mesh with I the geared portion of the flywheel 84. The

gear 101 is preferably an integral part of a bearing 160 which spins about the shaft 100, the bearing providing recesses for a plurality of roller bearings 132 and 133, as best shown in Fig. 12. A large gear 102 is also fixedly mounted upon the bearing 160 and so positioned as to'mesh with a gear 103. The gear 103 is mounted on an idler shaft 104, in mesh with a gear 105 forming part 'of the clutch mechanism 106, as best shown in Figs. 10, 11, and 12.

The clutch mechanism 106 is operable by the initial rotation of the trip shaft 81 to connect the shaft with the drive shaft 54. The shaft 81 is thereby caused to rotate in a direction opposite to the rotation caused by the pull on the rope 91.

The drive shaft 54 is constantly rotated in counter-clockwise direction, as indicated by the arrows in Figs. 10 and 11. A sleeve 111, having a splined connection with the shaft 54 and forming part of the clutch mechanism 106, is positioned on the shaft 54 adjacent the gear 105. An outer sleeve 110 is rotatably and slidably mounted on the sleeve 111. A nut 112, threaded on one end of the sleeve 111, forms a'stop for the sleeve 110. The end of the gear 105 is provided with a plurality of radially extending teeth 124, cooperating with similar teeth 125 formed 011 the outer face of a clutch ring 126. The clutch ring 126 is mounted on the sleeve 111 between friction rings 121 and 122. The

ring 126 is clamped between the friction rings 121 and 122 by a spanner nut 127 and a washer 128. A, spiral spring 129, positioned between the nut 127 and the end of the sleeve 110, normally retains the sleeve 110 in bearing contact with the nut 112. The rings 121 and 122 grip the clutch ring 126 sufliciently to cause the ring 126 to normally rotate with the inner sleeve 111 and shaft 54. The friction rings 121 and 122 provide a friction drive permitting clutch ring 126 to slip and to rotate relative to the shaft 54 upon the initial engagement of the rotating ring with the non-rotating toothed gear 105. The gear 105 is held against longitudinal movement on the shaft 54 by outer and inner collars 130 and 131, respectively, which are fixedly mounted on the shaft 54. The collars 130 and 131 are spaced apart sufficiently to permit the gear 105 to remain stationary on the rotating shaft 54. A plurality of roller bearings 107 provide for easy rotation or spinning of the gear 105 relative to the shaft 54.

The sleeve 110 is slidable to the right, as observed inFig. 12 by means of cam mechanism connected with the fly wheel 84. The rotation of the fly wheel 84, occasioned by the initial rotation of the trip shaft 81 as described, thereby moves the -toothed clutch ring 126 into operative engagement with the stationary toothed gear 105. The inertia of the gear 105 and of the mechanism connecting the gear with the shaft 81 tends to prevent .an immediate start at high speed and the resulting shock of the engagement of the clutch ring with the gear is minimized by the slipping of the ring 126 withinithe friction rings 121 and 122.

lltotation of the fly wheel 84 is utilized to slide the ring 126 into and out of operative engagement with the gear 105. For this purpose, the outer sleeve 110 has a downwardly projecting member 119 connected with a yoke 116 by means of a pin 1 20. The yoke 116 is pivotally connected with pins 117 forming part of a trunnion sleeve 123. An arm 118 projects from the yoke 116 into the path of cams 113 and 1,14 mounted on the outer periphery of the fly wheel 84. The movement of the fly wheel 84, occasioned by the rotation of the trip shaft 81 Carries the fly wheel to a point where the cam 114 operatively engages the arm 118. Engagement of the cam 114 and arm 118 moves the yoke 116 to the right, as observed in Fig. 12, carrying with it the outer sleeve 110 and the inner sleeve 111 to a point where the clutch ring 126 operatively engages the toothed gear 105, causing the gear to rotate with the shaft 54. The resulting rotation of the gear 105 starts the gear mechanism and the fly wheel 84 torotating in a direction opposite to that caused by the initial breaking down movement of the trip shaft 81, with the result that the fly wheel 84 is rotated back to the position shown in full line in Fig. 8. This return movement of the fly wheel 84 brings the pin 96 into contact with the upper end of the segmental slot 97 and thereby also rotates the disk 85 back to the position shown in Fig. 9. In rotating the disk 85 back to its original position, the cranks 82, links 83, and bearing members 79 are likewise returned to their full line position, carrying with them roller 64 to its original operative position.

The cam 114 is so positioned on the outer periphery of the fly wheel 84 as to immediately operatively connect the trip shaft 81 with the main shaft 54 upon the completion of the initial movement of the trip shaft occasioned by pulling the rope 91. The position of the cam 113 is such that the return movement of the fly wheel 84, occasioned by its operative engagement with the shaft 54, disengages the clutch mechanism 106, at substantially the same time that the roller 64 has been elevated to its normal operative position. In practice, the operator pulls the rope 91 at the instant when the remaining uncurved portion of the strip of material33 is of substantially the length desired for the tail 52. This results in the immediate lowering of the roller 64 and permits the remaining portion of the strip 33 to pass through the machine unaffected by the rollers. The coil 53vis shown above the line of travel of the strip 33, and it is desirable that the coil be lowered to a plane substantially identical with the line of travel of the strip.

ing means is operatively connected with the shaft 54 by a second clutch mechanism, generally designated in Figs. 7 and 13 by the numeral 135. The coil throwing means includes the curved throw plate 7 6 which is so mounted on the machine as to guide and support the 7 strip 33 as it is being coiled by turning backwardly upon itself as shown in Figs. 3 and 8. The coil 53 is also supported by the rotatable rollers 67 and 67a.

The plate 7 6 is also used to move the com- 30 pleted coil 53 from its full line position to its dotted line position of Fig. 8. The plate 76 has a pivotal mounting comprising a member 136 fixedly mounted on a shaft 137.

A crank 138, mounted on the shaft 137, is

operatively connected with a cam disk 139 by means of a link 140, as best shown in Fig. 3. A counter balance weight 146 has an arm 147 connected to the link 140 by means of bolts 148. One complete revolution of the disk 139 99 operates to move the plate 76 forwardly and to "return the plate to its upright position. The clutch mechanism 135 is provided to connect the disk 139 with the shaft 54 and to disconnect the disk and shaft u'pon completion of one revolution of the disk.

The disk 139 is journalled on a shaft 141 and has a sprocket wheel 143 fixedly mounted on its hub so that the wheel and the disk rotate together. The sprocket wheel 143 is 0;

connected with a sprocket wheel 145 by a sprocket chain 144. The sprocket wheel 145 is fixedly mounted on a clutch member 149 forming a portion of the clutch mechanism 135. The member 149 is journalled on the main drive shaft 54 and does not rotate therewith except when the member operatively engages a sleeve 156 having a splined connection with the shaft 54. The sleeve 156 is slidable on the shaft 154 so as to operatively engage and disengage the member 149, the sleeve having teeth adapted to engage corresponding teeth on the member.

A yoke member 150, best shown in Fig. 17

actuated by a cam connection with the disk 138, is operable to move the sleeve 156 to dis- "engage the member 149 upon completlon of one revolution of the disk. The yoke 150 is carried by brackets 151 and 152 suitably fastened to one of the standards 34, forminga portion of the frame of the machine. A- pm 153 provides a pivotal mounting for the yoke 150. The sleeve 156 is moved into operative engagement with the member 149 by means of a yoke 154. The yoke 154 is slidably mounted on a fixed shaft 180 and has a forked end operatively engaging the clutch mechanism by means of a pair of oppositely positioned bolts 175. A sleeve 173 is slidably mounted on the sleeve 156 and is ro- A spanner nut 167 and a washer 169 prevent tatable therewith. A key 172 provides a splined connection between the shaft 54 and the sleeve 156. A key 174 provides a similar splined connection between the sleeve 156 and the outer sleeve 173. The keys 172 and 174 cause the sleeves 156 and 173 to rotate with the shaft 54 and permit longitudinal movement of the sleeves relative to the shaft and to each other.

The sleeve 173 is ofiset at one end to provide a mounting for a ring 171 with which the yoke 154 is connected by the bolts 175.

the ring 171 from moving longitudinally on the sleeve 17 3 and permits rotation of the sleeve relative to the ring. This construction enables movement of the yoke 154 to actuate the entireclutch mechanism 135 other than the member 149, longitudinally of the shaft 54. An offset in the other end of the sleeve 173 provides a mounting for a ring 170 which is connected with the yoke 150 by a pair of oppositely positioned bolts 176. The ring 170 is held in its mounting by a spanner nut 168, the construction being such as to permit the sleeve 173 to rotate relative to the ring. It is obvious that rotation of the yoke 150 about its pivot 153 will move the entire clutch mechanism 135 longitudinally of the shaft 54. A spiral spring 177 having one end bearing against the spanner nut 168 and the other against a shoulder 178 on the sleeve 156, permits initial sliding movement of the sleeve 173 to occur in advance of a corresponding movement of the sleeve 156 towards the member 149. A cam member 155, mounted on the trip shaft 81 as shown in Figs. 17

and 18, causes the yoke 154 to move the sleeve 156 into operative engagement with the clutch member 149. This movement results from the initial rotation of the shaft 81 in the direction indicated by the arrows on Figs. 17

- and 18 and is occasioned by pulling on the rope 91. The pull on the rope 91 startsthe disk 139 to rotating and actuates the throw plate 76 at the same time that the roller 64 is being lowered. A sleeve member 181 is integrally formed with the yoke 154 and has a cam roller 182 mounted thereon so as to engage a cam surface 184 on a cam lever 183 when the shaft 81 starts its initial rotation. The lever 183 is pivotally mounted on the cam member 155 and is normally held in hearing engagement with a pin 186 by means of a spring 185. The initial rotation of the shaft 81 carries with it the lever 183, forcing the sleeve 181 and the yoke 154 to the left, as observed in Fig. 18. The described movement of the yoke 154 to the left also slides the toothed sleeve 156 along the shaft 54 into engagement with the toothed cam member149. The rotatiton of the shaft 81 in the direction indicated bythe arrow of F ig..18-ceases before the shaft has completed a revolution. Rotation of the shaft 81 in the opposite direction then begins as a result of the engagement of the fly wheel 84 with the drive shaft 54 through the medium of the clutch mechanism 106 in the manner already described. This reversed rotation of the shaft 81 carries with it the cam member 155 and also brings the lever 183 into direct contact with the roller 182 since the sleeve 181 has, in the meantime, returned to its original position. Upon contact of the end of the lever 183 with the under side of the roller 182, the spring 185 yields and permits the lever to slide over the outer end of the roller 182, to its original position, shown in full lines in Fig. 18, and in dotted lines in Fig. 17.

The above described movement of the sleeve 56 into engagement with the clutch member 149 carries with it the yoke 150 to the dotted line position shown in Fig. 13. The rotation of the disc 84, resulting from the engagement of the sleeve 156 with the clutch member 149, is utilized to disengage the member and sleeve upon completion of one revolution of the disc 84. For this purpose, the upper end of the yoke 150 is provided with a head 163 in which is mounted a pin 164. A fixed carriage guide 162, forms a mounting for a slidable-bar 159, with which the yoke 150 is connected by means of the pin 164. The ends of the pin 164 projectthrough a yoke 161. A second yoke 166 is positioned in the end of an aperture 187 formed in the slidable bar 159. The yoke 166 is held in bearing contact with the yoke 161 by a compression spring 188, mounted in the aperture 187. A cam roller 158 is mounted on the end of the slidable bar 159 in the path of a cam plate 157 which is secured to the disk 139 by a plurality of bolts 189. The bolts 189 have their heads positioned in an annular groove 190 formed in the outer periphery of the disc'139. The groove 190 has a T-shaped cross section and the bolts 189 are inserted in the groove through a slot 191 provided for that purpose.

The shanks of the bolts 189 project through the narrow open portion of the groove. The groove 190 extends entirely around the disk 139 and permits the cam plate 157 to be mounted at any desired point on the periphery of the disk.

Vhen the slidable portion of the clutch mechanism 135 is moved into'operative engagement with the clutch member 149, the yoke 150 is thereby moved to the dotted line position of Fig. 13, as already described, and carries with it the bar 159 to a point whe're the cam roller 158 is in the path of the cam plate 157. The rotation of the disk 139, occasioned by the engagement of the clutch mechanism 135, as already described, brings the cam plate 157 into contact with the roller 158 upon the completion of the revolution of the disk. This contact of the plate 157 with the roller 158 moves the yoke 150 from the dotted line position, shown in Fig. 13, to the full line position therein shown, thereby moving the slidable portion of the clutch mechanisms 135 out of engagement with the cam member 149 and stopping the disk 139. It is to be noted that the starting and stopping of the disk 139 also actuates the throw plate 7 6 forward and backward, thereby synchronizing the throwing of the coil 53, on to the platform 134 with the lowering of the roller 64.

Thus, it will be seen that improved means has been provided for imparting curvature to a strip of material which causes the strip to form a coil, and that by means of novel return roll mechanism, operating simultaneously with throw-plate mechanism, the substantially completed coil is removed from the machine with one uncurved end forming a coil.

Having thus described my invention, it is obvious that various immaterial modifications may be made in the same without departing from the spirit, of my invention; hence, I do not wish to be understood as limiting myself to the exact form, construction, arrangement, and combination of parts herein shown and described or uses mentioned.

What I claim as new and desire to secure by Letters Patent is: f

1. ln a coiling machine operable to curve a strip of material being fed therethrough in a generally horizontal direction, three rollers arranged in nesting spaced apartpyramidal relation with the upper tangential plane of the base rollers inclined upwardly in the direction of travel of thestrip, means operable to oppositely rotate the base and apex rollers, said apex roller being positioned relative to the base rollers to impart a single bending operation to the strip, and means operable to drop the forward one of said base rollers to a position where the curving operation ceases.

2. In a machine'of the kind described, a constantly rotating drive shaft, a plurality of rollers actuated by said drive shaft, a collapsible supporting member for one of said rollers, means operable to cause the collapse of said member, clutch mechanism operable to connect the member with the drive shaft, said connection causing the return of said member to its uncollapsed position, cam mechanism operable by the collapse of said member to operatively engage said clutch H mechanism with said shaft, and means operable to disengage said clutch member upon return of the supporting member to uncollapsed position.

3. In a coiling machine operable to curve a strip of material being fed therethrough in a generally horizontal direction, three rollers arranged in nesting spaced apart relation with the upper tangential plane of the base rollers inclined upwardly in the path of the strip, means operable to rotate the rollers, the

apex roller rotating oppositely to the base to collapse under the weight of said roller clutch mechanism operable to return sa1 member and roller to their original position, cam mechanism operable by the collapse of said member to operatively engage said clutch mechanism with said shaft, and means operable to disengage said clutch mechanism upon return of said supporting member to,

uncollapsed position. a

4. In a machine of the kind described, a plurality ofrollers arranged in pyramidal relation, a collapsible supporting member for one of said rollers, a constantly rotating main drive shaft, a normally stationary trip shaft,

rotation of the trip shaft in one direction causing the collapse of said supporting member and rotation in the opposite direction returning said member'to uncollapsed position,

means operable to impart initial rotation to the trip shaft to: cause the collapse of said member, mechanism operable by said initial rotation of the trip shaft to operatively connect said shafts, said mechanism being actuated by such connection with the main drive shaft to rotate the trip shaft back to the uncollapsed position of the supporting member.

5. In a'coiling machine operable to curve a strip of material being fed-therethrough in a generally horizontal direction, three rollers arranged in nesting spacedapart pyramidal relation, the upper tangential plane of the 'base rollers being inclined upwardlyin thedirectionof travel of the strip, a drive shaft, mechanism operativelyconn'ecting said rollers with the shaft, the apex roller rotating oppositely to the base rollers, mechanism op; erable to move the forward one of said rollers into and out off the path 'of the strip, said mechanism comprising pivotalbearings for said forward roller, a trip shaft, knuckle mechanism normally supporting said forward roller on said trip shaft in the path of said strip, means operable to rotate the trip shaft and cause the collapse of the knuckle mechanism, a clutch mechanism operable to connect the trip shaft with the driving shaft, thereby causing the trip shaft to return said knuckle mechanism to its. original non-collapsed position, cam mechanism operable by the collapse of said knuckle mechanism to operatively engagesaid clutch member with said shaft, and means operable to disengage said clutch member upon return of said knuckle "mechanism to uncollapsed position.

.6. Ina machine of the kind described, a plurality of rollers arranged in pyramidal relation, a collapsible supporting member for one of said rollers, a constantly rotating main drive shaft, a normally stationary trip shaft,

rotation of the trip shaft in one direction causing the collapse of said supporting mem member, mechanism operable by said initial ber and'rotation in the opposite direction'returning said member to uncollapsed position, means operable to impart initial rotation of the trip shaft to cause the collapse of said able to \curve a strip of material fed therethrough, a constantly rotating drive shaft, a plurality of rollers actuated by said drive shaft, a collapsible supporting member for one of said rollers, a trip shaft operable to cause the collapse of said supporting member, mechanism operable by the collapse of said supporting member to connect said supporting member with the drive shaft, said connectionrotating the trip shaft sufficiently to return said supporting member to its uncollapsed position, means operable to advance the coiled strip upon collapse of said supporting member, and clutch mechanism operable to connect and disconnect said means with the drive shaft upon movement of the supporting member to collapsed and uncollapsed positions respectively.

8. In a machine of the kind described, a plurality of rollers arranged to curve a strip of material fed therebetween and to cause said strip to form a coil on a supporting member adjacent said rollers, a swingplate operable to propel the coil, a constantly rotating drive shaft, an intermittently operable trip shaft, means operable to impart a partial rotation to the trip shaft in one direction and to release the strip from said rollers, clutch mechanism operable bysaid initial rotation of the trip shaft to connect the trip shaft with the drive shaft, the connection of the shafts causing the trip shaft to reversely rotate back toits original position, actuating means operable to advance and return the swing plate, a second clutch mechanism operable by the initial rotation of the trip shaft to connect said actuating means with the main drive shaft, and cam mechanism operable to di engage said second clutch mechanism upon the return of the swing plate t9 its original position.

9. In a machine of the kind described, a

constantly rotating drive shaft, a plurality of rollers actuated by said drive shaft to coil a strip of material fed therethrough, a collapsible supporting member for one of said rollers, means operable to cause the collapse of said supporting member, mechanism operable by the collapse of said supporting memment to connect said supporting member with the drive shaft, said connection causing the return of said supporting member to its uncollapsed position, a pivotally mounted plate operableto remove the strip of material from the machine, and clutch mechanism actuated by said member collapsing means to rotate said plate forwardly and backwardly in synchronization with the collapse and return of the supporting member to uncollapsed vwhen said roller is moved to its inoperative position, clutch mechanism operable to operatively engage said means with said shaft, cam means operable by the collapse of said support to move said clutch mechanism to operatively engage said first mentioned means with said shaft, and cam means operable to release said clutch mechanism upon the return of said support to uncollapsed position.

11. In a machine of the kind described, a drive shaft, a plurality of rollers actuated by said shaft and positioned to curve a strip of material fed therethrough, a collapsible support for one of said rollers, means operable to cause the collapse of said support, the rollers being inoperative to advance and curve the strip when said su port is collapsed, clutch mechanism opera le to connect said shaft and support, can mechanism operable by the collapse of said support to operatively engage said clutch mechanism with said shaft, said connection causing the return of said support to its uncollapsed position, means operable to move the entire strip of material forwardly when said roller is moved to its inoperative position, a second clutch mechanism operable to operatively engage said means with said shaft and a second cam mechanism operable to disengage said second clutch mechanism from said shaft.

12. In a machine of the kind described, a constantly rotating drive shaft, a plurality of rollers actuated by said shaft and positioned to curve a strip of material fed therethrough,

'a collapsible supporting member for one of said rollers, a trip shaft operable to actuate said supporting member to collapsed and uncollapsed positions, clutch mechanism operable to connect said shafts, said connection causing the return of said supporting member to its uncollapsed position, cam mechanism operable by the ,collapse of said supporting member to operatively engage said clutch mechanism with said drive shaft, means operable to move the entire strip of material forwardly when said supporting member is collapsed, a second clutch mechanism operable to operatively engage said means said shaft and cam means operable to disen- I gage said second clutch mechanism when said supporting member returns to uncollapsed position.

13. In a coiling machine operable to advance a strip of material therethrough, a pair of rollers arranged inv parallel relation, a

third roller spaced apart, from and nesting between said pair of rollers to permit a strip of material to pass therebetween, a main drive shaft, gear mechanism operable by said shaft to drive the rollers, the forward one of the pair of rollers being mounted to rotate about said shaft as an axis, jointed supports for said last mentioned roller means operable to break said jointed supports and permit said roller to rotate out of the path of said strip, means operable to return said jointed supports to their upright position, and clutch mechanism operable to engage and disengage said means with'said shaft.

In witness whereof, I hereunto subscribe my; name this 27th day of November A. D. 19 9.

CHARLES D. DALLAS. 

